Automatic universal profile and die sinking machine



Dec. 27, 1938. B s ss 2,142,061

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AUTOMATIC UNIVERSAL PROFILE AND DIE SINKING MACHINE Original Filed Oct. 8, 1934 17 Sheets-Sheet 6 Dec. 27, 1938. B. 'sAssEN 2,142,061

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AUTOMATIC UNIVERSAL PROFILE AND DIE SINKING MACHINE Original Filed Oct. 8, 1934 17 Sheets-Sheet 8 Dec. 27, 1 938. B. SASSEN 2,142,061

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AUTOMATIC UNIVERSAL PROFILE AND DIE SINKING MACHINE Original Filed Oct. 8, 1954 17 sheeis -sheet 11 Dec. 27, 1938. B. SASSEN 2,142,061

AUTOMATIC UNIVERSAL PROFILE AND DIE SINKING MACHINE ori inal Filed Oct. 8, 1954 17 Sheets-Sheet 1s 47 awn/Mow 4 BER/ED517555 waz MWMW Dec. 27, 1938.

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Dec. 27, 1938. s ss 2,142,061

AUTOMATIC UNIVERSAL'PROFILE AND DIE SINKING MACHINE Original Filed Oct. 8, 1934 17 Sheets-Sheet 1e BEKNHRD 5/1555 Dec. 27, 1938. B. SASSEN 2,142,061

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Ratenied Dec. 27, 1938 Ziiifii PATENT: OFFICE AUTOMATIC UNIVERSAL PROFILE AND D SINKING MACHINE Bernard Sassen, Cincinnati, Ohio, assignor to The Cincinnati Milling Machine Company, Cincinnati, Ohio, a corporation of Ohio Application October '8, 1934, Serial No. 747,267 Renewed August 19, 1987 100 Claims.

This invention relates to machine tools and more particularly to improvements in pattern It is an object of this invention to provide a general purpose pattern controlled machine tool which may be selectively set up to operate under any one of a plurality of methods whereby with the work at hand may be utilized.

Another object of this invention is to provide a profiling machine which maybe selectively operated for automaticcontrol by a pattern; or manually controlled with or without the assistance of a pattern.

A further object of this invention is to providea machine of the class described which; for diesinking purposes, may be selectively operated either by the reciprocating method or the rotary method and under either automatic or manual control.

An additional object of this invention is to provide an improved hydraulically operable mechanism for remotely controlling the position of a part, such as the pump displacement control pendulum.

Other objects of this invention are to improve the accuracy of slide movements, increase the :25 selectivity of cutter spindle speeds, and generally improve the speed and accuracy of operation of the machine.

Other objects and advantages of the present invention should be readily apparent by reference '1') to the following specification considered in conjunction with the accompanying drawings illustrative of one embodiment thereof, but it will be understood that any modifications may be made in the specific structural details thereof within 43 the scope of the appended claims without departing from or exceeding the spirit of the invention.

Referring to the drawings in which like reference numerals indicate like or similar parts:

Figure 1 is a front elevation of a machine embodying the principles of this invention.

Figure 1A is a detail of the tracer head handwheel.

Figure 2 is a plan view of the machine shown in Figure 1.

like and involving three dimensional movements. 7

' a single machine the method most suitable for Figure 3 is a side elevation of the machine shown in Figure 1 and as viewed from the right of that figure.

Figure 4 is a section on the line 4-4 of Figure 2. 5

Figure 4A is a detail section on the line 4A-4A of Figure 4.

Figure 5 is a horizontal section on the line 5-5 of Figure 1 showing the variable delivery pump mechanism.

Figure 6 is a vertical section on the line 6-6 of Figure 5 showing more particularly the variable delivery pump block.

Figure 7 is a section through the tracer head on the line 7-1 of Figure 5.

Figure 8 is a similar section taken on the line 8-8 of Figure 5.

Figure 9 is a section on the line 9-9 of Figure 4 showing the variable speed hydraulic unit for the spindle.

Figure 10 is a section on the line ill-Ill of Figure 9 showing the start and stop control mechanism for the spindle.

Figure 11 is a section on the line l'l-l i of Fig:

ure 5 showing the details of the tracer head rotating motor.

Figure 12 is a section on the line i2-l2 of Figure 11.

Figure 13 is a section on the line iii-l3 of Figure 11. i

Figure 14 is a detail section on the line li-M of Figure 4.

Figure 15 is a section on the line l5-l5 of Figure 11.

Figure 16 is an enlarged detail of the ratchet pawl as viewed on the line l6-l 6 of Figure 15.

Figure 17 is an enlarged detail of a portion of Figure 14 showing the relative position of the ratchet pawl control plunger.

Figure 18 is a section through the vertical ram operating cylinder as viewed on the line I 8-l8 of Figure 2. Figure 19 is a detail section on the line I9-l9 of Figure 18. 1

Figure 20 is a section on the line 20-20 of Figure 19.

Figure 21 is a section on the line 2l-2i of Figure 19.

Figure 21A is a section on the line 2lA-2IA of Figure 19.

Figure 22 is a detail section on the line 22-22 of Figure 1 showing the details of the feed rate control mechanism.

Figure 23 is a section on the line 23-23 of Figure 22.

Figure 24 is a partial side elevation of the machine shown in Figure l as viewed from the left of that figure.

Figure 25 is an enlarged detail section as viewed on line 25-25 of Figure 24.

Figure 26 is an enlarged view of the spindle rate dial.

Figure 27 is a horizontal section through the main valve control block as viewed on the line 21-21 of Figure 1.

Figure 28 is a section on the line 22-2! Figure 1.

Figure 29 is a section on the line 29-29 Figure 1.

Figure 30 is a section on the line Ill-30 Figure 1.

Figure Figure 1.

Figure 32 is a section on the line 22-32 Figure 1. r

Figure 33 is a section on the line 3333 Figure l.

Figures 34 to 42 inclusive are sections through 31 is a section on the line 8l-3l of I the valve control block taken on the respective section lines as indicated in Figure 28.

Figure 43 is a diagram of the hydraulic control circuit of the machine.

Figure 44 is a diagrammatic view of the circuit for remotely controlling the position of the pump pendulum control pin.

Figure 45 is a diagrammatic view showing movements of tracer and cutter in effecting engagement with the pattern and work.

Figure 46 is a sectional view on line 46-46 of Figure 5.

Figure 47 is a section on line "-41 of Figure 46.

Figure 48 is an enlarged view of the control panel.

Figure 49 is a section on the line 49-49 of Figure 44.

Figure 50 is a section on the line 50-50 of Figure 44.

Figure 51 is a view showing uses of bars for changing profile.

Automatic pattern controlled machine tools are utilized for forming surfaces in conformity to a prescribed master and usually comprise a first pair of relatively movable elements, such as a cutter and a work support, and a second pair of relatively movable elements such as a tracer and a pattern support, and means for effecting relative movement between the elements of each pair in such a manner as to produce a profiling action. An analysis of a profiling action will show that a profile or contour is produced by the summation of the instantaneous components of the instantaneous relative movements between the elements of each pair in two right i angular paths, and that three-dimensional surfaces are produced by periodically effecting a third relative incremental movement between the elements of each pair in a direction normal to the plane containing said right angular paths.

In practice it is well-known that in machines of various types in connection with which this invention may be applied, that the elements may be variously supported to effect these movements, and in some cases the tracer and cutter may move while the work and master remain stationary or vica versa; whereas in other cases the tracer and work, or the pattern and cutter, may be stationary, and the remaining elements of each pair the movable ones, or the reverse of either of these. Additionally, one or more movements may be impartedtoeitherelementofeachpairandthe remaining movement or movements imparted to the remaining element of each pair. Furthermore, the plane which contains the two right angular paths referred to above may be any plane in space, and the third movement will always be in a direction normal to this plane. It should also be obvious that in producing the relative movement between the cutter and work in the two right angular paths, that this may involve either a lateral movementor an axial movement of the cutter spindle. ways of embodying these elements in a machine are contemplated within the scope of this invention, because the improved means disclosed herein for effecting the various relative movements may be suitably applied regardless of which element or elements do the moving or regardless of the actual planes in space to which the various relative movements may be allocated. Since no useful purpose would therefore be served by showing all of these various forms, only one embodiment of the invention is illustrated in the drawings.

Referring to Figures 1, 2 and 3 of the drawings, the reference numeral 5' indicates the bed of the machine having guideways 5| formed in the front portion thereof for guiding a reciprocable slide'ii suitable for receiving work and pattern. The bed also has a second set of guideways it formed thereon at a higher elevation than the guideways II for supporting and guiding a hori-- zcntal reciprocable ram 54. The ram in turn, as more particularly shown in Figure 2, has verticalguideways 55 formed on the forward end thereof for receiving and guiding a vertically movable slide 58 which, in the present machine, carries the tracer 5i and the cutter 58. It will thus be seen that movement of the table, while the other slides are stationary, establishes a rectilinear cutting path which is of course parallel to the direction of table movement. If the table remains stationary and the ram 54 is moved, a rectilinear cutting path will be established which is perpendicular to the first described cutting path. Additionally, a simultaneous movement of both slides will result in a cutting path which is at an angle to the two previously described cutting paths, and this angle will vary in accordance with the ratio of the relative rates of movement of the two slides.

Viewed in another way, it will be seen that simultaneous movement of the vertical slide 58 and the table 52 will result in a cutting path which is at an angle to the surface of the work table and the amount of this angle will also vary in accordance with the ratio of the relative rates of movement of the two slides. From this it will be seen that various combinations of movements are possible and that a suflicient variety of cutting paths can be established depending upon the nature of the work to be performed.

The work table 52 is moved by means of a fluid motor, either a rotary type for effecting relative movement between a screw or nut, or reciprocating type, such as shown, comprising a cylinder 59, having a contained piston 60, which is connected by piston rod ii to opposite ends of the table 52. It will be noted that the piston rod extends through opposite ends of the cylinder so that the volumes of flow to and from the cylinder will always be equal. The motor is provided with two ports 82 and 63 which are connected by channels 84 and 65 respectively to op posite ends 66 and 61 of a reversible variable de- All of these various forms or livery pump 88 whereby opposite rotation of the pump will eflect opposite movements of the motor and thereby the slide or table.

The horizontal ram 54 is moved by a similar hydraulic motor comprising a cylinder 89 having a contained piston I0, as more particularly shown in Figure 4, the piston being connected by a piston rod II to a fixed part of the bed 00. In this instance, the cylinder 88 moves with the ram, and the piston and piston rod are stationary.

'It will be noted in this instance that the piston tegral with the horizontal ram 54 and has a contained piston 18 operatively connected by the piston rod 19 to the vertical slide 00.

Spindle transmission and control mechanism The spindle transmission is more. particularly shown in Figure 4 and is driven by an hydraulic unit indicated generally by the reference numeral 80. This unit is supplied with fluid pressure from a pump 82 which is mounted coaxially along with pump 8| for actuation in tandem bya prime mover such as the electric motor 83. All of these parts are carried in the rear end of the ram 54 as more particularly shown in Figures 2 and 3.

The pumps are supplied from a reservoir 84 located in the bottom of the bed 50. It will be noted from Figure 3 that the pumps 8i and 82 are located a considerable distance above the reservoir and in order to lower the hydraulic lift and still make it possible to ascertain the fluid level, an auxiliary reservoir 85 is provided near the top of the bed 50. This reservoir is connected to the main reservoir by channel 85' having a needle valve 86' therein. For this auxiliary reservoir to be effective, it is necessary of course that the reservoir tank 84 be absolutely closed. A flexible supply pipe 86 serves to connect the reservoir 84 with the pumps 8i and 82 and this flexible pipe is filled with fluid up to the level indicated by the line 81 which is the same plane as the level 88 of the fluid in the auxiliary reservoir 05. The reservoir system is filled through an opening in the top of the auxiliary reservoir and this opening is closed by the cover 89. A gauge glass 90 is also associated with the auxiliary reservoir to indicate the fluid level. By this construction it is only necessary for the pumps to lift the fluid from the level 81 up to the pumps which is comparatively short, considering the distance between the level 81 and the main reservoir 84. The ram 54 is provided with a collecting chamber 9I as indicated in Figure 4 which serves to collect fluid from this portion of the machine and return it to the main reservoir through a flexible pipe 92 as indicated in Figure 3. The needle valve is opened only during filling of the machine, and after filling the tanks and pipes to the level indicated by glass 90, the valve is closed.

The pump 82 is connected by the channel 88, through a starting control valve I43, Figures 10 and 43, to the intake port 94 of the variable speed hydraulic unit 80 for supplying fluid pressure thereto. This intake port may be in the form of an elbow 95, Figure 4, threaded in one end oi a sleeve 98 which is held against rotation by means 01' a rod 96A depending between a pair of adlustable screws 98B mounted in fixed bosses as shown in Figure 14. The other end of the sleeve has an elbow 81 threaded therein to which is connected the exhaust channel 98. The sleeve has a bore 88 formed in one end thereof and a similar bore I formed in the other end thereof, but these bores as will be noted from Figure 4 do not intersect one another.

Near the inner end of the pressure bore 99 are a plurality ofslots IOI which are evenly spaced circumferentially as indicated in Figure 9. Similarly, the bore I00 has a plurality of evenly spaced slots I02, but these slots are positioned circumferentially so as to lie in planes intermediate to the planes of the slots IIII. It will be noted from Figure 4 that the inner end of the slots I02 overlaps the slots IOI so that they will alternately register with the radially extending channels I08 which alternately serve as supply and exhaust channels for the reciprocating pistons of the motor. v

The pistons, such as I04 and I05, are arranged in pairs so that each pair of pistons is supplied through a common channel, such as I03. A cylinder block I06 which carries all of the pistons, is attached, as by bolts I01, to a second sleeve member I08, rotatable about the inner sleeve 98, and has a gear I09 attached to one end which, through a pinion IIO, actuates the spindle transmission. All'of the pistons lying in the plane of the piston' I04 engage a cam member III, as indicated in Figure 9, and react against this cam member to effect rotation of the gear I09. Similarly, the pistons lying in the plane of cylinder I engage the periphery of a second cam member II2 having the same formation as'the cam III. Each of these cams has five lobes, although any other suitable number may be utilized. The number of lobes must correspond, however, to the number of slots in the sleeve. The cam member III is integral with one face of a gear H3 mounted for rotation on the anti-friction bearings II4. similarly, the cam member I I2 is carried on one face of a gear II5 also mounted for rotation on the anti-friction bearings I I6.

The gear H3 and thereby the cam III is adjusted by a worm II I secured to one end of a shaft H0, and the gear II5-is rotated by a worm II9 secured to one end of a shaft I20. As shown in Figure the shafts I I8 and I20 are each provided with intermeshing gears I2I and I22 so that upon rotation of the shaft H8, as by the manual control lever I23, both cams will be simultaneously adjusted. The connections, and so forth, between the manual control lever and the cams is suchthat the two cams will be exactly in phase with one another at either extreme position of the handle I23, and will be in opposite phase at an intermediate position of the handle. Since there are five lobes this means that the included angle of one lobe is 72 degrees and if one cam is moved 18 degrees clockwise and the other cam moved 18 degrees counter-clockwise, the cams will be in opposite phase. The other condition will be when the first cam is rotated counter-clockwise and the second cam clockwise. These adjustments make it possible to vary the rate of speed and direction of rotation of the hydraulic unit.

The mode of operation of this hydraulic unit is as'follows. The pump 82 is a constant delivery pump and is driven by the electric motor 

